EP3396191B1 - Kupplungsmechanismus, insbesondere für kraftfahrzeug - Google Patents

Kupplungsmechanismus, insbesondere für kraftfahrzeug Download PDF

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Publication number
EP3396191B1
EP3396191B1 EP18166193.5A EP18166193A EP3396191B1 EP 3396191 B1 EP3396191 B1 EP 3396191B1 EP 18166193 A EP18166193 A EP 18166193A EP 3396191 B1 EP3396191 B1 EP 3396191B1
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EP
European Patent Office
Prior art keywords
rotation
pressure plate
threaded rod
mechanism according
ratchet wheel
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EP18166193.5A
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English (en)
French (fr)
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EP3396191A1 (de
Inventor
Nicolas Deliencourt
Benoit Perry
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Valeo Embrayages SAS
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Valeo Embrayages SAS
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Publication of EP3396191A1 publication Critical patent/EP3396191A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate

Definitions

  • the present invention relates to a clutch mechanism, in particular for a motor vehicle.
  • the present invention relates to a wear-catching clutch mechanism, in particular for a motor vehicle.
  • a clutch device conventionally comprises a reaction plate, a clutch mechanism comprising a movable pressure plate, and a friction disk mounted between said reaction and pressure plates.
  • the movement of the pressure plate is controlled by a diaphragm, itself controlled by a clutch abutment.
  • the pressure plate is thus movable between a clutch position in which the friction disk is clamped between said pressure and reaction plates, and a disengaging position in which the friction disk is released.
  • the use of the clutch device causes wear of the friction disc liners and the counter-materials of the associated pressure and reaction plates. This results in a variation of the position of the pressure plate relative to the associated diaphragm and / or with respect to the reaction plate, generating a variation of the friction disk clamping force and a modification of the licking point and the stroke of the clutch stop. It is recalled that the licking point is the position from which a torque can be progressively transmitted through the clutch device.
  • a clutch device with catch-up wear is known from the document FR 2,765,287 in the name of the Claimant.
  • This document discloses a wear-compensating clutch device for a motor vehicle, comprising a pressure plate intended to bear against a friction disc of the clutch device, a diaphragm serving to actuate the pressure plate between a position totally engaged in which said pressure plate is pushed against the friction disk, and a fully disengaged position in which said pressure plate is moved away from the friction disk by means of return means of the pressure plate.
  • the pressure plate, the friction disk and the diaphragm are housed in a cover which is fixed with respect to the reaction plate.
  • the device further comprises a compensating member of the wear of the friction disc, interposed between the diaphragm and the pressure plate, and movable in rotation about an axis in a determined range, said catch member comprising a co-operating ramp. with a counterbeam formed or integral with the pressure plate, so as to adjust the distance between the diaphragm and the pressure plate and compensate for the wear of the friction disk as a function of the position of the ramp relative to the counter-pressure. ramp.
  • the clutch device further comprises displacement means comprising a ratchet wheel adapted to pivot about an axis mounted on a cassette.
  • the displacement means also comprise an elastic member fixed on the cassette, said elastic member having an actuating zone cooperating with the ratchet wheel so as to actuate the pivoting of the ratchet wheel in case of wear.
  • the actuation zone is formed on an actuating member of the elastic member.
  • the ratchet wheel is coupled in rotation to a worm mounted around the aforementioned axis and meshing with a toothed sector secured to the catch member.
  • the rotation of the ratchet wheel causes the retraction member to move in order to compensate for the wear.
  • the elastic member is actuated by the diaphragm, during its displacement between its engaged and disengaged positions.
  • the document DE 10 2008 051 100 discloses a wear-catching clutch device in which the displacement means the wear compensating member comprises a threaded rod pivotally mounted in a cassette, said cassette being secured to the pressure plate.
  • the threaded rod is secured to a ratchet wheel driven in rotation by an elastic member.
  • the threaded rod cooperates with a threaded carriage secured to the catch member.
  • the invention aims to provide a device and a clutch mechanism of simple structure, economical and reliable.
  • the nut can be mounted in a cassette attached to the ramp means or the pressure plate.
  • the cassette can form a support for holding the nut in circumferential position on the ramp means or on the pressure plate, while allowing the rotation of the nut about the axis of the latter.
  • the cassette may comprise a base from which extend two flanks circumferentially spaced relative to each other, the nut being mounted circumferentially between the sides of the cassette.
  • flanks allow to circumferentially hold the nut in position while the base can be used for fixing the cassette on the ramp means or on the pressure plate, directly or indirectly.
  • the threaded rod can be rotated by the cassette.
  • the threaded rod can be stopped in rotation to any other element integral with the ramp means or the pressure plate.
  • the threaded rod can pass through the nut.
  • the threaded rod can be stopped in rotation by shape cooperation between the threaded rod and at least one of the sides of the cassette.
  • the shape cooperation can be achieved using a flat or a finger engaged in a groove.
  • the nut may comprise drive means formed at its outer periphery, the drive means of the nut comprising a ratchet wheel cooperating with latching means, said latching means being able to actuate the rotation of the latch. the ratchet wheel in case of wear of the friction disc.
  • the ratchet wheel and the nut can form a single piece, or be formed by two parts integral with each other, for example.
  • the latching means may comprise an elastic member comprising an actuating zone held in abutment on a toothing of the ratchet wheel.
  • the elastic member may be elastically deformable.
  • the threaded rod can pass through the ratchet wheel.
  • the mechanism may comprise anti-rotation means adapted to allow the rotation of the nut and / or the ratchet wheel in a single direction of rotation.
  • the elastic member may comprise an actuating member on which the actuation zone is formed.
  • the anti-rotation means may comprise at least two resilient strips, held in abutment on the toothing of the ratchet wheel, in zones situated at different distances from each other with respect to the axis of rotation. of the ratchet wheel.
  • the threaded rod may comprise a portion engaged in a groove of the pressure plate, said groove extending in the radial direction with respect to the axis of rotation of the ramp means.
  • the corresponding portion of the threaded rod tends to move along the groove during relative movement of the threaded rod relative to the nut, i.e. as the wear of the threaded disc increases. friction is compensated.
  • the threaded rod may be adapted to be moved in a translational motion relative to the ratchet wheel.
  • the threaded rod may comprise a portion engaged in an opening of the ramp means.
  • the threaded rod may have a bent portion, said bent portion being inserted into the opening of the ramp means.
  • Said opening of the ramp means may extend along the axis of rotation of the ramp means.
  • the invention also relates to a device comprising a clutch mechanism of the aforementioned type, characterized in that it comprises a reaction plate and a friction disk, the pressure plate being movable relative to the reaction plate, between a position engaged in which the friction disc is clamped between the pressure plate and the reaction plate, and a disengaged position, in which the friction disk is released.
  • the Figures 1 to 10 illustrate a clutch mechanism and a clutch device according to a first embodiment of the invention.
  • the clutch device 1 comprises an annular fixed cover 2 of axis X, intended to be fixed on a reaction plate 3, and an annular pressure plate 4 and movable along the axis X with respect to the reaction plate 3 and to the cover 2.
  • a friction disc 5 is intended to be interposed axially between the pressure plate 4 and the reaction plate 3.
  • the friction disc 5 comprises a support 6 on either side of which are fixed friction linings 7.
  • the cover 2 has an annular portion 8 extending generally radially and a generally cylindrical portion 9, extending axially from the radially outer periphery of the radial annular portion 8.
  • the device 1 further comprises a diaphragm 10 comprising a deformable annular portion 11, in the manner of a Belleville washer, from which actuating fingers 12 extend radially inwards.
  • the radially inner periphery of the fingers 12 is adapted to cooperate with a clutch abutment, as is known per se.
  • the diaphragm 10 is mounted in abutment on the cover 2, at the level of bearing zones 13.
  • the bearing zones 13 are distributed around the circumference and are formed by zones projecting from the radial annular portion 8 of the cover 2.
  • the diaphragm 10 is centered by means of studs 14 or rivets, fixed on the radial part 8 of the cover 2.
  • the diaphragm 10 is held in abutment on said bearing areas 13 of the cover 2, by means of a support member formed here by a rigid washer 15 fixed to the stud opposite the lid 2 with respect to the diaphragm 10, and an elastic member, formed here by a washer 16 elastically deformable.
  • the spring washer 16 is supported on the one hand on the rigid washer 15 and on the other hand on the diaphragm 10, so as to exert a return force on the diaphragm 10, tending to keep it resting on the zones of support 13 of the lid 2.
  • Such a rigid washer 15 and such an elastic washer 16 are particularly known from the document WO2008 / 125780 .
  • the diaphragm 10 serves to actuate the pressure plate 4 between a fully engaged position in which said pressure plate 4 is pushed towards the reaction plate 3, so as to grip the friction disc 5 between said plates 3, 4, and a disengaged position in which said pressure plate 4 is spaced from the reaction plate 3 so as to release the friction disc 5.
  • tabs resilient 17 able to exert an axial force connect the cover 2 and the pressure plate 4.
  • the tabs 17 are arranged to resiliently bias the pressure plate 4 to its disengaged position.
  • the tongues 17 also provide a rotational coupling between the cover 2 and the reaction plate 3, on the one hand, and the pressure plate 4, on the other hand.
  • Wear compensating means are interposed axially between the pressure plate 4 and the diaphragm 10. More particularly, the diaphragm 10 cooperates with said wear compensating means in an area located radially outwardly of the zones. support 13 of said diaphragm 10 on the lid 2.
  • These means comprise a movable catch member 18 in the form of a ring and having an end 19 against which the diaphragm 10 is able to bear, and an end 20 having at least one ramp 21 extending circumferentially, cooperating with an associated counter ramp 22 formed directly on the pressure plate 4.
  • each ramp 21 of the catch member 18 and the associated counter ramp 22 of the pressure plate 4 is between 2 ° and 12 °.
  • the catch member 18 forms ramp means.
  • Displacement means make it possible to rotate the catch member 18 about the X axis in case of wear of the friction disc 5.
  • the displacement means comprise a ratchet wheel 23 having an external toothing 24 and an internal tapping so as to form a nut, and a rod 25 comprising a threaded zone 26 cooperating with the ratchet wheel 23.
  • the nut 13 comprises drive means formed on its outer periphery.
  • the ratchet wheel 23 is mounted in a cassette 27 forming a support.
  • the cassette 27 comprises a flat base 28, from which two flanks 29 extend, perpendicular to the base 28 (see in particular figure 4 ).
  • the flanks 29 extend radially.
  • the base 28 has two lateral zones 30 extending circumferentially beyond the flanks 29. Said lateral zones allow the cassette 27 to be fastened to the catching member 18 by means of screws.
  • the flanks 29 have holes 31 allowing the threaded rod 25 to pass therethrough.
  • the threaded rod 25 and at least one of the holes 31 have at least one zone 32 of non-circular cross-section so as to stop the cassette 27 in rotation. the threaded rod 25 (see in particular Figures 6 to 8 ).
  • the ratchet wheel 23 is mounted circumferentially between the flanks 29 while being able to pivot about its axis, around the threaded rod 25.
  • the ratchet wheel 23 bears on one of the flanks 29, directly or through the intermediate of a friction washer.
  • An elastic element such as for example a helical compression spring 33, is mounted between the other sidewall 29 and the ratchet wheel 23, so as to keep the ratchet wheel 23 resting on the opposite sidewall 29.
  • the threaded rod 25 has a first portion 25a and a second portion 25b extending perpendicularly relative to each other.
  • the first portion 25a comprises the threaded zone 26 engaged in the tapping of the ratchet wheel 23, the first portion 25a passing through the holes 31 of the flanks 29.
  • the free end of the second portion 25b is engaged in a groove 34 of the rim plate. pressure 4.
  • the displacement of the threaded rod 25 relative to the cassette 27 thus causes the retraction member 18 to rotate relative to the pressure plate 4, so that the end 19 of the retraction member 18 moves axially apart. of the pressure plate 4, so as to compensate for the wear of the friction disc 5.
  • the displacement means further comprise an elastic member 35 which is elastically deformable.
  • the elastic organ also referred to below as ratchet 35, comprises (see in particular figure 3 ) a first axially extending portion 36 fixed to the base of the cassette 27, for example by means of rivets, a second portion 37 extending radially outwardly from the first portion 36, and a third portion 38 forming an actuating member, extending axially from the second portion 37, the free end of the third portion 38 forming an actuating zone 39 held in abutment on the toothing 24 of the ratchet wheel 23.
  • connection zone 40 between the second portion 37 and the third portion 38 of the pawl 35 bears on the radially outer periphery of the diaphragm 10.
  • the pawl 35 is actuated by the displacement of the diaphragm 10 between its engaged and disengaged positions.
  • the pawl 35 elastically spaced from its rest position during the actuation of the diaphragm 10 to its engaged position.
  • the friction disk 5 has a certain amount of wear and when the pawl 35 is actuated, the pawl 35 jumps a tooth 24 in the disengaged position after having turned the ratchet wheel slightly in the engaged position so that, on the next activation of the ratchet ratchet 35, the actuating zone bears on the shoulder formed between two teeth 24 so as to rotate the ratchet wheel 23 about its axis.
  • Such pivoting of the ratchet wheel 23 occurs in the clutch phase.
  • the diaphragm 10 plates the catch member 18 bearing on the pressure plate 4, so that the catch member 18 can not pivot relative to the pressure plate 4.
  • the threaded rod 25 can not move in translation along the axis of the first part 25a, relative to the cassette 27, and the ratchet wheel 23 moves in translation relative to the threaded rod 25, along the axis of the ratchet wheel 23.
  • the ratchet wheel 23 is thus driven by a movement helical pattern combining a rotational movement about its axis, around the portion 25a of the threaded rod, and a translation movement relative to the threaded rod 25. Such a translational movement compresses the elastic element 33.
  • the diaphragm 10 releases the retraction member 18.
  • the elastic element 33 pushes the ratchet wheel 23 in translation against the corresponding flank 29 of the cassette 27. causes the translational displacement of the threaded rod 25 relative to the cassette 27 and, due to the connection between the threaded rod 25 and the pressure plate 4, the rotation of the catch member 18 on which is fixed to the cassette 27, with respect to the pressure plate 4.
  • FIGS. 9 and 10 represent the position of the threaded rod 25 and the catch member 18 relative to the pressure plate 4, respectively in the absence of wear of the friction disc 5 and for a worn friction disc 5.
  • FIGS. 11 to 23 illustrate a clutch mechanism and a clutch device 1 according to a second embodiment of the invention.
  • the ratchet wheel 23 is held in abutment on the sidewalls 29 of the cassette 27, without the interposition of an elastic element 33.
  • the ratchet wheel 23 is able to bear on the flanks 29 of the cassette 27, possibly by means of one or more friction washers.
  • the base of the cassette 27 is fixed to the pressure plate 4, here by riveting, for example.
  • the first portion 25a of the threaded rod 25 is engaged in a tapping of the ratchet wheel 23, which thus forms a nut capable of pivoting about its axis, the second portion 25b of the threaded rod 25 being engaged in a opening 41 of the catch member 18.
  • Said opening 41 is rectilinear and extends along the axis X.
  • Said opening 41 is formed in a large area (along the X axis) of the catch member 18 , that is to say at a so-called lower end of a ramp 21.
  • the threaded rod 25 is, as previously, rotated by the flanks 29 of the cassette 27, by shape cooperation, for example by means of a flat.
  • the mechanism further comprises anti-rotation means 42 adapted to allow the rotation of the ratchet wheel 23 in a single direction of rotation.
  • the anti-rotation means 42 comprise two parts each in the form of a sheet 43, said sheets 43 being stacked one on the other, each sheet 43 having several adjacent elastic strips 44 whose free ends are able to bear on the toothing 24 of the ratchet wheel 23.
  • the ends of said lamellae 44 are elastically supported on the toothing 24 of the ratchet wheel 23, in zones situated at different distances from each other with respect to the axis of rotation of the ratchet wheel 23. Said ends are able to slide on the teeth 24 in a first direction of rotation of the ratchet wheel 23 and are able to block the rotation of the ratchet wheel 23 in a second direction of rotation. of the ratchet wheel 23, by pressing on the shoulders formed in the bottom of the teeth 24.
  • the plates 43 are fixed to the pressure plate 4, for example by riveting.
  • Such anti-rotation means 42 may also be provided in the embodiment described with reference to Figures 1 to 10 .
  • the mechanism according to the second embodiment may be devoid of such anti-rotation means 42.
  • the pawl 35 comprises a body 45 extending radially fixed, for example by riveting, on the radial annular portion of the cover 2, and an actuating tongue 46 extending axially from the body, in the direction of the ratchet wheel 23. ( figure 17 ).
  • the free end of the actuating tongue 46 forms an actuating zone 39 adapted to cooperate with the toothing 24 of the ratchet wheel 23.
  • the elasticity of the pawl 35 keeps the actuating zone 39 resting on the toothing 24.
  • the pawl 35 comprises a bearing portion 47 extending radially from the body 45 of the pawl 35, in the direction of the diaphragm 10.
  • the bearing portion 47 is offset radially inward with respect to the zone d 39.
  • the bearing portion 47 is able to bear on the diaphragm 10, in particular on the radially outer periphery of the diaphragm 10.
  • the bearing portion 47 is adjustable along the axis X of the mechanism to define the angular position of the diaphragm 10 relative to the cover 2 in the engaged position, the wear compensating system being in a stabilized position.
  • the bearing portion 10 is able to bear on the ramp means, in particular on the catch member 18.
  • the figure 17 represents the mechanism in the engaged position and in new condition. In this position, the free end 39 of the actuating tongue 46 is held elastically bearing on the toothing 24 of the ratchet wheel 23, at the end of a tooth 24, without however jumping the tooth 24.
  • the pawl 35 slides on the ratchet wheel 23 by the value of a tooth, until the abutment 47 comes into contact with the diaphragm 10.
  • the pawl 35 is then driven by the pressure plate 4 so that there is no more relative movement between the actuating zone 46 of the pawl 35 and the ratchet wheel 23. There is no longer any possible rotation of the ratchet wheel 23.
  • the pressure plate 4 is released in the disengagement phase so that it deviates from the reaction plate 3 by the action of the elastic return tongues 17. The relative movements allow to maintain the actuation zone 39 of the pawl 35 on the same tooth 24 of the ratchet wheel 23.
  • the figure 18 illustrates the mechanism being disengaged and the figure 19 illustrates the mechanism in the fully disengaged position.
  • the actuating tongue 46 is held elastically bearing on the toothing 24 of the ratchet wheel 23, without jumping tooth 24.
  • the end 39 of the actuating tongue 46 jumps a tooth 24, as shown in FIG. figure 20 .
  • the ratchet wheel is rotated by pressing the end 39 into the shoulder formed in the bottom of the corresponding tooth 24.
  • the rotation of the ratchet wheel during this disengaging phase causes the displacement of the threaded rod and, thus, the rotation of the catch member 18, because of the connection at the portion 25b of the threaded rod 25 and the opening 41 of the wear-compensating member 18.
  • the figure 21 illustrates the mechanism at the end of this wear-compensating phase.
  • the Figures 22 and 23 represent the position of the threaded rod 25 and the catch member 18 relative to the pressure plate 4, respectively in the absence of wear of the friction disc 5 and for a worn friction disc 5.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Claims (15)

  1. Kupplungsmechanismus, insbesondere für ein Kraftfahrzeug, der aufweist:
    - einen Deckel (2),
    - eine Druckplatte (4), die bezüglich des Deckels (2) gemäß einer Achse (X) des Mechanismus beweglich und dazu bestimmt ist, mit einer Reibscheibe (5) zusammenzuwirken,
    - eine zwischen einer eingerückten und einer ausgerückten Stellung bewegliche Membran (10), die die Verschiebung der Druckplatte (3) in Gang setzen kann,
    - zwischen die Membran und die Druckplatte eingefügte Verschleißnachstelleinrichtungen, wobei die Nachstelleinrichtungen Rampeneinrichtungen (18, 21), die mit Gegenrampeneinrichtungen (4, 22) zusammenwirken, damit die Drehung der Rampeneinrichtungen (18, 21) bezüglich der Gegenrampeneinrichtungen (4, 22) den Abstand zwischen der Membran (10) und der Druckplatte (3) verändert, und Drehantriebseinrichtungen der Rampeneinrichtungen (18) aufweisen, wobei die Antriebseinrichtungen eine Mutter (23) aufweisen, die gemäß einer Hauptachse (L) mit einer Gewindestange (25) zusammenwirkt,
    dadurch gekennzeichnet, dass die Mutter (23) mit den Rampeneinrichtungen (18) bzw. mit der Druckplatte (4) verbunden und fähig ist, um ihre Hauptachse (L) zu schwenken, wobei die Gewindestange (25) in die Druckplatte (4) bzw. in die Rampeneinrichtungen (18) eingeführt ist, um die Drehung der Rampeneinrichtungen (18) bezüglich der Druckplatte (4) durch Drehung der Mutter (23) um die Gewindestange (25) zu bewirken, wobei die Gewindestange gemäß der Hauptachse (L) in Drehung fest ist.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Mutter (23) in eine Kassette (27) montiert ist, die an den Rampeneinrichtungen (18) oder an der Druckplatte (4) befestigt ist.
  3. Mechanismus nach Anspruch 2, dadurch gekennzeichnet, dass die Kassette (27) eine Basis (28) aufweist, von der ausgehend sich zwei Flanken (29) erstrecken, die in Umfangsrichtung voneinander entfernt sind, wobei die Mutter (23) in Umfangsrichtung zwischen den Flanken (29) der Kassette (27) montiert ist.
  4. Mechanismus nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Stange (25) durch die Kassette (27) in Drehung angehalten wird.
  5. Mechanismus nach den Ansprüchen 3 und 4, dadurch gekennzeichnet, dass die Gewindestange (25) durch Formzusammenwirkung zwischen der Gewindestange (25) und mindestens einer der Flanken (29) der Kassette (27) in Drehung angehalten wird.
  6. Mechanismus nach Anspruch 5, dadurch gekennzeichnet, dass die Formzusammenwirkung mit Hilfe einer Abflachung oder eines in eine Rille eingeführten Fingers hergestellt wird.
  7. Mechanismus nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Mutter (23) an ihrem Außenumfang geformte Antriebseinrichtungen enthält, wobei die Antriebseinrichtungen der Mutter ein mit Einrasteinrichtungen (35) zusammenwirkendes Klinkenrad (23) aufweisen, wobei die Einrasteinrichtungen (35) die Drehung des Klinkenrads (23) im Fall des Verschleißes der Reibscheibe (5) in Gang setzen können.
  8. Mechanismus nach Anspruch 7, dadurch gekennzeichnet, dass die Einrasteinrichtungen ein elastisches Organ (35) aufweisen, das einen Ingangsetzungsbereich (39) enthält, der in Auflage auf einer Zahnung (24) des Klinkenrads (23) gehalten wird.
  9. Mechanismus nach einem der Ansprüche 7 oder 8, dadurch gekennzeichnet, dass die Gewindestange (25) durch das Klinkenrad (23) verläuft.
  10. Mechanismus nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass er Drehhemmungseinrichtungen (42) aufweist, die die Drehung der Mutter (23) und/oder des Klinkenrads (23) nur in einer Drehrichtung erlauben können.
  11. Mechanismus nach Anspruch 10, dadurch gekennzeichnet, dass die Drehhemmungseinrichtungen (42) mindestens zwei elastische Lamellen (44) aufweisen, die in Auflage auf der Zahnung (24) des Klinkenrads (23) in Bereichen gehalten werden, die sich in unterschiedlichen Abständen zueinander bezüglich der Drehachse des Klinkenrads (23) befinden.
  12. Mechanismus nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die Gewindestange (25) einen Teil (25b) aufweist, der in eine Rille (34) der Druckplatte (4) eingeführt ist, wobei die Rille (34) sich in der radialen Richtung bezüglich der Drehachse (X) der Rampeneinrichtungen (18) erstreckt.
  13. Mechanismus nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die Gewindestange (25) einen Teil (25b) aufweist, der in eine Öffnung (41) der Rampeneinrichtungen (18) eingeführt ist.
  14. Mechanismus nach Anspruch 13, dadurch gekennzeichnet, dass die Gewindestange (25) einen gebogenen Abschnitt (25b) aufweist, wobei der gebogene Abschnitt (25b) in die Öffnung (41) der Rampeneinrichtungen (18) eingeführt ist.
  15. Mechanismus nach einem der Ansprüche 13 oder 14, dadurch gekennzeichnet, dass die Öffnung (41) der Rampeneinrichtungen (18) sich gemäß der Drehachse (X) der Rampeneinrichtungen (18) erstreckt.
EP18166193.5A 2017-04-26 2018-04-06 Kupplungsmechanismus, insbesondere für kraftfahrzeug Active EP3396191B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1753627A FR3065766B1 (fr) 2017-04-26 2017-04-26 Mecanisme d'embrayage, notamment pour vehicule automobile

Publications (2)

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EP3396191A1 EP3396191A1 (de) 2018-10-31
EP3396191B1 true EP3396191B1 (de) 2019-05-15

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FR (1) FR3065766B1 (de)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2765287B1 (fr) * 1997-06-17 1999-09-17 Valeo Embrayage a friction a dispositif de rattrapage d'usure, en particulier pour vehicule automobile
FR2914032B1 (fr) 2007-03-23 2009-06-05 Valeo Embrayages Embrayage a diaphragme comprenant une articulation de diaphragme.
DE112008002711B4 (de) * 2007-10-31 2020-01-02 Schaeffler Technologies AG & Co. KG Reibungskupplung mit Rampensystem zum Ausgleich eines bei Verschleiß auftretenden Fehlabstands zwischen Druckplatte und Hebelsystem
DE102011087994A1 (de) * 2011-12-08 2013-06-13 Schaeffler Technologies AG & Co. KG Nachstelleinrichtung für eine Reibungskupplung und entsprechende Reibungskupplung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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FR3065766A1 (fr) 2018-11-02
EP3396191A1 (de) 2018-10-31
FR3065766B1 (fr) 2019-04-26

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